CN101143600A - Real wheel toe angle control system of vehicle - Google Patents
Real wheel toe angle control system of vehicle Download PDFInfo
- Publication number
- CN101143600A CN101143600A CNA2007100079916A CN200710007991A CN101143600A CN 101143600 A CN101143600 A CN 101143600A CN A2007100079916 A CNA2007100079916 A CN A2007100079916A CN 200710007991 A CN200710007991 A CN 200710007991A CN 101143600 A CN101143600 A CN 101143600A
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- China
- Prior art keywords
- tooth bar
- vehicle
- right sides
- control system
- actuator
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Classifications
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
- B62D—MOTOR VEHICLES; TRAILERS
- B62D17/00—Means on vehicles for adjusting camber, castor, or toe-in
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G3/00—Resilient suspensions for a single wheel
- B60G3/18—Resilient suspensions for a single wheel with two or more pivoted arms, e.g. parallelogram
- B60G3/20—Resilient suspensions for a single wheel with two or more pivoted arms, e.g. parallelogram all arms being rigid
- B60G3/26—Means for maintaining substantially-constant wheel camber during suspension movement ; Means for controlling the variation of the wheel position during suspension movement
- B60G3/265—Means for maintaining substantially-constant wheel camber during suspension movement ; Means for controlling the variation of the wheel position during suspension movement with a strut cylinder contributing to the suspension geometry by being linked to the wheel support via an articulation
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G17/00—Resilient suspensions having means for adjusting the spring or vibration-damper characteristics, for regulating the distance between a supporting surface and a sprung part of vehicle or for locking suspension during use to meet varying vehicular or surface conditions, e.g. due to speed or load
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G3/00—Resilient suspensions for a single wheel
- B60G3/18—Resilient suspensions for a single wheel with two or more pivoted arms, e.g. parallelogram
- B60G3/20—Resilient suspensions for a single wheel with two or more pivoted arms, e.g. parallelogram all arms being rigid
- B60G3/22—Resilient suspensions for a single wheel with two or more pivoted arms, e.g. parallelogram all arms being rigid a rigid arm forming the axle housing
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
- B62D—MOTOR VEHICLES; TRAILERS
- B62D5/00—Power-assisted or power-driven steering
- B62D5/04—Power-assisted or power-driven steering electrical, e.g. using an electric servo-motor connected to, or forming part of, the steering gear
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
- B62D—MOTOR VEHICLES; TRAILERS
- B62D5/00—Power-assisted or power-driven steering
- B62D5/04—Power-assisted or power-driven steering electrical, e.g. using an electric servo-motor connected to, or forming part of, the steering gear
- B62D5/0421—Electric motor acting on or near steering gear
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
- B62D—MOTOR VEHICLES; TRAILERS
- B62D7/00—Steering linkage; Stub axles or their mountings
- B62D7/06—Steering linkage; Stub axles or their mountings for individually-pivoted wheels, e.g. on king-pins
- B62D7/14—Steering linkage; Stub axles or their mountings for individually-pivoted wheels, e.g. on king-pins the pivotal axes being situated in more than one plane transverse to the longitudinal centre line of the vehicle, e.g. all-wheel steering
- B62D7/146—Steering linkage; Stub axles or their mountings for individually-pivoted wheels, e.g. on king-pins the pivotal axes being situated in more than one plane transverse to the longitudinal centre line of the vehicle, e.g. all-wheel steering characterised by comprising means for steering by acting on the suspension system, e.g. on the mountings of the suspension arms
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
- B62D—MOTOR VEHICLES; TRAILERS
- B62D7/00—Steering linkage; Stub axles or their mountings
- B62D7/06—Steering linkage; Stub axles or their mountings for individually-pivoted wheels, e.g. on king-pins
- B62D7/14—Steering linkage; Stub axles or their mountings for individually-pivoted wheels, e.g. on king-pins the pivotal axes being situated in more than one plane transverse to the longitudinal centre line of the vehicle, e.g. all-wheel steering
- B62D7/15—Steering linkage; Stub axles or their mountings for individually-pivoted wheels, e.g. on king-pins the pivotal axes being situated in more than one plane transverse to the longitudinal centre line of the vehicle, e.g. all-wheel steering characterised by means varying the ratio between the steering angles of the steered wheels
- B62D7/1581—Steering linkage; Stub axles or their mountings for individually-pivoted wheels, e.g. on king-pins the pivotal axes being situated in more than one plane transverse to the longitudinal centre line of the vehicle, e.g. all-wheel steering characterised by means varying the ratio between the steering angles of the steered wheels characterised by comprising an electrical interconnecting system between the steering control means of the different axles
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G2202/00—Indexing codes relating to the type of spring, damper or actuator
- B60G2202/30—Spring/Damper and/or actuator Units
- B60G2202/31—Spring/Damper and/or actuator Units with the spring arranged around the damper, e.g. MacPherson strut
- B60G2202/312—The spring being a wound spring
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G2204/00—Indexing codes related to suspensions per se or to auxiliary parts
- B60G2204/40—Auxiliary suspension parts; Adjustment of suspensions
- B60G2204/419—Gears
- B60G2204/4192—Gears rack and pinion
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G2401/00—Indexing codes relating to the type of sensors based on the principle of their operation
- B60G2401/17—Magnetic/Electromagnetic
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Transportation (AREA)
- Vehicle Body Suspensions (AREA)
- Power Steering Mechanism (AREA)
- Steering-Linkage Mechanisms And Four-Wheel Steering (AREA)
Abstract
A rear wheel toe angle control system is used as an actuator for controlling rear wheels of a vehicle. The control system is an electric-powered for rapid operation thereof, thereby providing handling stability. The left and right rear wheels are operated by the single actuator to reduce weight and manufacturing costs of a vehicle, and toe angles of the left and right rear wheels are identically controlled to improve handling stability of a vehicle.
Description
Technical field
The present invention relates to the vehicle dynamic control that a kind of dynamics by control vehicle improves operational stability, more specifically, the real wheel toe angle control system that relates to a kind of vehicle, wherein angle of toein is according to two variable trailing wheels of the motoring condition of vehicle, handle by independent reducing gear, the angle of toein that makes two trailing wheels thus is synchronously always being changed constantly, and vehicle can reduce its size and weight.
Background technology
Generally, the suspension that is installed on the vehicle is set between car body and the wheel, and uses one or more connecting rods that two rigid bodies are connected to each other.Described suspension comprises trailing arm (trailing arm), steering swivel, Control arm etc.
Described suspension absorbs the irregular input of the ground-surface that occurs in the wheel driving process effectively, in providing the traveling comfort of taking.In addition, described suspension is suitably controlled rocking of the car body that brought by the manipulation of chaufeur or Uneven road, so give the chaufeur facility.In addition, when wheel travelled on up-and-down road surface, suspension made the vertical load on the tire contacting surface remain on proper level, thereby guaranteed vehicle handling and stability when turn inside diameter or brake.
Meanwhile, work as Ackermann steer angle because the speed of a motor vehicle or and the road surface between friction, it can be turned excessively or understeer, so damaged vehicle handling and stability.In order to address this problem, the Korean Patent No.511742 that the applicant obtains discloses a kind of angle of toein control system (AGCS: how much control system of Active Suspension) of trailing wheel in (on August 25th, 2005), at the angle of toein of Ackermann steer angle control trailing wheel, improve the dynamic control and the road-holding property of vehicle by the length of controlling the back Control arm.
Fig. 1 is the real wheel toe angle control system according to the vehicle of prior art.With reference to Fig. 1, the angle of toein control system 20 of trailing wheel comprises a pair of actuator 22 and 23 that is installed in two ends, after cross member 12 left and right sides respectively, with connecting rod 26 and 27, described connecting rod is used for connecting actuator 22 and 23 and left and right sides trailing wheel 14 and 15, and changes the angle of toein of left and right sides trailing wheels 14 and 15 by the bar for the treatment of translation 24 that is installed to actuator 22 and 23 and 25.
So traditional real wheel toe angle control system 20 of the vehicle of structure is in Ackermann steer angle operated actuator 22 and 23, to prevent the excessive or understeer of Vehicular turn.
Simultaneously, the applicant has developed a kind of real wheel toe angle control system of vehicle recently, wherein for the angle of toein of fast control trailing wheel 14 and 15, improves the slow problem of response of hydraulic actuator, has used electric actuator.
In electric actuator, the limit sensors of Hall element type has been installed on the top of shell, and this sensor comprises that Hall element and permanent magnet are stably to control the position of described bar.Install around permanent magnet by the track (guide) that non-magnetic material is made, to improve the perception of Hall element by the magnetic flow of concentrating described permanent magnet.Described electric actuator is made like this, described track slidably in conjunction with the inside face of described shell to guide the motion of translation of described bar.
The aforementioned real wheel toe angle control system of vehicle (wherein actuator be installed in the trailing wheel crossbeam about part) control is just at the foreign steamer angle of toein of turning vehicle, with the oversteer phenomenon of control vehicle when turning, thereby the friction force between tire and the road surface and the yawing velocity of control vehicle have been increased.
Yet traditional real wheel toe angle control system 20 of described vehicle is provided with two actuators 22 and 23 that are used for controlling left and right sides trailing wheel 14 and 15.Therefore, because narrow installing space, have restriction on the actuator 22 and 23 installing, and two actuators 22 and 23 weight and the manufacturing cost of vehicle have been increased.In addition, because use described two actuators 22 and 23 in the prior art, left and right sides trailing wheel 14 may be controlled differently with 15 angle of toein, causes the instability control of vehicle stability.
Summary of the invention
The objective of the invention is to solve the above-mentioned problems in the prior art.An object of the present invention is to provide a kind of angle of toein control system of trailing wheel, wherein for being used for the actuator of control vehicle trailing wheel, used electric actuator to be used for the quick operation of trailing wheel, so guarantee the stability of operating, left and right sides trailing wheel is operated reducing the weight and the manufacturing cost of vehicle by single actuator, and the angle of toein of similarly controlling left and right sides trailing wheel is to improve the operational stability of vehicle.
According to one aspect of the present invention to achieve these goals, a kind of real wheel toe angle control system of vehicle is provided, comprise left and right sides trailing wheel by the crossbeam support of vehicle; Left and right sides link member, an end of each link member is connected to left and right sides trailing wheel; Two ends are connected respectively to the tooth bar of left and right sides link member; Be installed on the crossbeam to hold the shell of described tooth bar; Be installed in the actuator to cooperate with it on the tooth bar, described actuator moves tooth bar, so left and right sides link member changes the angle of toein of left and right sides trailing wheel simultaneously.Actuator comprises the CD-ROM drive motor that is installed in the outer cover; Make the Ring gear of its rotation by CD-ROM drive motor; With described Ring gear ingear first miniature gears; With the rotating shaft that is installed to first miniature gears and with tooth bar ingear second miniature gears.
The real wheel toe angle control system of vehicle can also comprise the limit switch that is installed in the described shell, to detect the shiftable haulage line of described tooth bar, when the examined end of tooth bar is placed on initial position or excessive position of moving, the operation of described limit switch control actuator.In addition, the real wheel toe angle control system of vehicle also comprises the magnetic rings of the rotating shaft that is installed to first and second miniature gearss; With the magnetic pickup device that is installed on the outer cover of described Ring gear, to detect the magnetic force of magnetic rings, wherein utilize tooth pitch according to the tooth of the transmitting ratio of first gear and Ring gear and tooth bar and second miniature gears than the reduction ratio that obtains, measure the linear displacement of tooth bar by the amount of spin of conversion magnetic rings.
Description of drawings
From the explanation of the following preferred embodiment that provides in conjunction with the accompanying drawings, above and other objects of the present invention, feature and advantage will become obviously, wherein:
Fig. 1 is the figure that illustrates according to the real wheel toe angle control system of the vehicle of prior art;
Fig. 2 is the figure that illustrates according to the real wheel toe angle control system of vehicle of the present invention;
Fig. 3 is the perspective illustration of expression according to the real wheel toe angle control system of vehicle of the present invention;
Fig. 4 is the section drawing that illustrates according to the main portion of the real wheel toe angle control system of vehicle of the present invention.
The explanation of preferred embodiment
Below, describe the preferred embodiments of the present invention with reference to the accompanying drawings in detail.
Fig. 2 is the figure of the real wheel toe angle control system of expression vehicle of the present invention, Fig. 3 is the perspective illustration according to the real wheel toe angle control system of vehicle of the present invention, and Fig. 4 is the section drawing of expression according to the main portion of the real wheel toe angle control system of vehicle of the present invention.
With reference to Fig. 2 to 4, the left and right sides trailing wheel 54 of vehicle and 55 is being suspended in midair by after cross member 52.At this moment, trailing wheel 54 and 55 is connected to steering swivel 56, and described steering swivel is supported and supported by the longitudinal direction of trailing arm (not drawing) at vehicle by the horizontal direction of Control arm 57 at vehicle.In addition, each steering swivel 56 is supported at vertical direction by spring 58 and bumper 59.
Meanwhile, real wheel toe angle control system 60 is installed to left and right sides trailing wheel 54 and 55, to change the angle of toein of trailing wheel 54 and 55 when the Vehicular turn.
Real wheel toe angle control system 60 comprises and crossbeam 52 parallel housing mounted 66 and the tooth bar 67 that is accommodated in the shell 66.Described tooth bar 67 is supported in the shell 66 movably, and a plurality of rack tooth 67a is formed on the surface of tooth bar 67.
In addition, a pair of link member 64 and 65 that is connected to left and right sides trailing wheel 54 and 55 is connected to the two ends of tooth bar 67 respectively. Link member 64 and 65 is movably mounted, and each link member can be made up of one or more element, and its center of turn can be fixed on a side of crossbeam 52.
Simultaneously, link member 64 and 65 is controlled the angle of toein of left and right sides trailing wheel 54 and 55 by translation tooth bar 67.For this reason, for translation tooth bar 67, actuator 62 is installed.
Therefore, when actuator 62 work, mobile rack 67 makes link member 64 and 65 motions, changes the angle of toein of left and right sides trailing wheel 54 and 55 thus simultaneously.That is, when Vehicular turn, according to steering direction, one in the left and right sides trailing wheel 54 and 55 becomes toeing-in, and another becomes the wheel posterior cord, so the stability of control steered wheel.
Actuator 62 comprises outer cover 621 and is installed in CD-ROM drive motor 622 in the described outer cover 621.In addition, the gear unit 623b with predetermined length is formed on the rotating shaft 623a of CD-ROM drive motor 622, and Ring gear 624 is connected with gear unit 623b.In addition, first miniature gears 625 meshes with the wheel tooth of Ring gear 624.At this moment, the Ring gear 624 and first miniature gears 625 have the oblique tooth of reservation shape, described shape standard up to specification.In addition, second miniature gears 627 is connected to an end of the rotating shaft 626 of first miniature gears 625.Second miniature gears 627 meshes with the rack tooth 67a of tooth bar 67.At this moment, first and second miniature gearss 625 and 627 rotating shaft 626 are supported rotationally by the bearing 628 that is installed to outer cover 621.
In addition, CD-ROM drive motor 622 is electro-motors, preferably the DC motor.In this embodiment, CD-ROM drive motor 622 turns round with 10 to 16V DC input voitage and the specified input voltage of 13.5V.
At this moment, in shell 66, limit switch is set, is used to limit the stroke range of tooth bar 67.Described limit switch is installed in the described shell 66 to detect the mobile alignment of tooth bar 67.
In addition, described limit switch detects an end of tooth bar 67, and then, when tooth bar 67 was placed on its initial position, limit switch was set the reference position of tooth bar 67.And if the described end of tooth bar 67 is moved too much, the operation of limit switch control actuator 62 stops.
According to the real wheel toe angle control system 60 of the vehicle of above-mentioned structure, single actuator 62 causes left and right sides trailing wheel 54 and 55 to be changed together, so improved the reliability of Stability Control.In addition, because initial reference position and the too much mobile limited switch in position detect, so further improve the reliability of Stability Control and the operational stability of bringing thus.
In addition, provide the magnetic rings 626a in the rotating shaft 626 that is installed in described first and second miniature gearss 625 and 627, and the magnetic pickup device 629 that is installed to the described outer cover 621 that surrounds Ring gear 624 is provided, to detect the magnetic force of magnetic rings 626a.Therefore, can be from the rotation amount of magnetic rings 626a, the ratio of number of teeth between first miniature gears 625 and the Ring gear 624, and the tooth pitch of the rack tooth 67a of tooth bar 67 and second miniature gears 627 is than the linear displacement of measuring tooth bar 67.
In addition, described magnetic rings 626a is installed in the rotating shaft 626 of first and second miniature gearss 625 and 627, purpose is to measure the amount of spin of CD-ROM drive motor 622.In addition, in order to detect the magnetic force of magnetic rings 626a, magnetic pickup device 629 is installed to the outer cover 621 that surrounds Ring gear 624, near certain position of magnetic rings 626a.In addition, the magnetic signal that is detected by magnetic pickup device 629 is transmitted to the central processing unit of vehicle, and described central processing unit is calculated the amount of spin of the rotating shaft 623a that is caused by CD-ROM drive motor 622.
At this moment, the linear displacement of tooth bar 67 can be by measuring like this, promptly measure the amount of spin of magnetic rings 626a, utilize tooth pitch according to the rack tooth 67a of the ratio of number of teeth of first miniature gears 625 and Ring gear 624 and tooth bar 67 and second miniature gears 627 than the reduction ratio that obtains then, change described amount of spin.In addition, according to the linear displacement control left and right sides trailing wheel 54 of the tooth bar of measuring 67 and 55 angle of toein.
So the operation of the real wheel toe angle control system of the vehicle of structure is described below.
When vehicle ' particularly turns to since the gravity of car body or with the ground-surface friction force, its may understeer or ovdersteering.At this moment, the actuator 62 of operation real wheel toe angle control system 60 prevents Vehicular turn deficiency or ovdersteering.More specifically, if to CD-ROM drive motor 622 supplying power of actuator 62, CD-ROM drive motor 622 rotations are also transmitted rotational force and are given Ring gear 624.In addition, the rotation of Ring gear 624 makes and 625 rotations of Ring gear 624 ingears first miniature gears, is rotated so process rotating shaft 626 is connected to second miniature gears 627 of first miniature gears 625.Second miniature gears 627 meshes with the tooth of tooth bar 67, so be rotated, tooth bar 67 is moved.At this moment, according to the reduction ratio of Ring gear 624 and first and second miniature gearss 625 and 627, can control the output of actuator 62.As mentioned above, by actuator 62 at left and right sides either direction mobile rack 67, so the link member 64 and 65 that is connected to left and right sides trailing wheel 54 and 55 is moved.Therefore, link member 64 and 65 is controlled the angle of toein of left and right sides trailing wheel 54 and 55 simultaneously, and causes that one in them becomes toeing-in, and another becomes the wheel posterior cord, so prevent Vehicular turn deficiency or ovdersteering.
Promptly, become toe-in by wheel by actuator 62 control outsides, the wheel of the inside becomes posterior cord, real wheel toe angle control system 60 control vehicles by Vehicular turn the time suspension posterior cord that the produces fugitiveness that causes, so guarantee Stability Control and the operational stability of therefore guaranteeing vehicle by the friction force between tire and the road surface.
At this moment, according to the linear displacement may command trailing wheel 54 of tooth bar 67 and 55 angle of toein.For this reason, magnetic pickup device 629 is measured the magnetic force of the magnetic rings of the rotating shaft 626 that is installed in first and second miniature gearss 625 and 627, determines the amount of spin of CD-ROM drive motor 622 thus by the amount of spin of magnetic rings 626a.Then, utilize according to the tooth of ratio of number of teeth between first miniature gears 625 and the Ring gear 624 and tooth bar and the tooth pitch between second miniature gears 627 than the reduction ratio that obtains, by the amount of spin of conversion driving motor, the linear displacement of measurement tooth bar 67.
Simultaneously, the initial start position of tooth bar 67 is set by described limit switch, so the stroke range of tooth bar 67 is accurately controlled.In addition, limit switch detects the end of tooth bar 67 and controls the operation of actuator 62, so tooth bar 67 can exceedingly not move.
According to the real wheel toe angle control system of the present invention of structure like this, the angle of toein of trailing wheel is quick on the draw operates electric actuator manipulation rapidly, thereby has improved operational stability.In addition, because by single actuator operated left and right sides trailing wheel, the control of the angle of toein by left and right sides trailing wheel has further improved operational stability.In addition, the real wheel toe angle control system size is little, so guarantee to be easy to install and reduced vehicle weight and manufacturing cost.In addition, because actuator is used for coming transmission of drive force by the combination of Ring gear and miniature gears, described propulsive effort can accurately and not transmit with losing.In addition, control system of the present invention is by the output of the control of the reduction ratio between regulating ring generating gear and miniature gears actuator.
As mentioned above, be illustrated, but the invention is not restricted to previous embodiment and accompanying drawing with reference to accompanying drawing according to the real wheel toe angle control system of vehicle of the present invention.In not breaking away from the claim restricted portion, those those skilled in the art can make various improvement and conversion is conspicuous.
Claims (3)
1. the real wheel toe angle control system of a vehicle, it comprises:
The left and right sides trailing wheel that supports by the crossbeam of vehicle;
Left and right sides link member, each link member have an end that is connected to left and right sides trailing wheel;
Two ends are connected to the tooth bar of left and right sides link member respectively;
Be installed to described crossbeam to hold the shell of described tooth bar; With
Be installed to the actuator of described tooth bar to cooperate with it, described actuator moves tooth bar, so that left and right sides link member changes the angle of toein of left and right sides trailing wheel simultaneously,
Wherein said actuator comprises: be installed in the CD-ROM drive motor in the outer cover; The Ring gear that makes it to rotate by described CD-ROM drive motor; With described Ring gear ingear first miniature gears; With the rotating shaft that is installed to first miniature gears and with described tooth bar ingear second miniature gears.
2. real wheel toe angle control system as claimed in claim 1, also comprise the limit switch that is installed in the described shell with the mobile alignment that detects tooth bar, when the examined end of tooth bar was positioned at initial position or excessive position of moving, described limit switch was controlled the operation of described actuator.
3. real wheel toe angle control system as claimed in claim 1 or 2 also comprises the magnetic rings of the rotating shaft that is installed to first and second miniature gears; And be installed to around the magnetic pickup device of the described outer cover of described Ring gear, to detect the magnetic force of described magnetic rings, wherein, utilization than the reduction ratio that obtains, is measured the linear displacement of described tooth bar according to the tooth pitch of the tooth of the ratio of number of teeth of first gear and Ring gear and tooth bar and second miniature gears by the amount of spin of conversion magnetic rings.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| KR1020060087860 | 2006-09-12 | ||
| KR1020060087860A KR100748350B1 (en) | 2006-09-12 | 2006-09-12 | Rear wheel toe angle control systems of the vehicles |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN101143600A true CN101143600A (en) | 2008-03-19 |
Family
ID=38602577
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNA2007100079916A Pending CN101143600A (en) | 2006-09-12 | 2007-02-01 | Real wheel toe angle control system of vehicle |
Country Status (5)
| Country | Link |
|---|---|
| US (1) | US7325818B1 (en) |
| EP (1) | EP1900603A1 (en) |
| JP (1) | JP2008068853A (en) |
| KR (1) | KR100748350B1 (en) |
| CN (1) | CN101143600A (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101628528B (en) * | 2009-05-15 | 2011-03-23 | 邵延 | Wheel link structure |
| CN104512456A (en) * | 2013-09-27 | 2015-04-15 | 北汽福田汽车股份有限公司 | Automobile, power steering gear, and control method of power steering gear |
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| JP4448838B2 (en) * | 2006-08-25 | 2010-04-14 | 本田技研工業株式会社 | Vehicle toe angle variable control device |
| JP2008055921A (en) * | 2006-08-29 | 2008-03-13 | Honda Motor Co Ltd | Variable rear wheel toe angle control device for vehicle |
| KR101316421B1 (en) | 2007-08-31 | 2013-10-08 | 현대자동차주식회사 | Active controlling method of steering for vehicle |
| EP2210796B1 (en) * | 2008-03-10 | 2011-08-17 | Honda Motor Co., Ltd. | Rear wheel steering vehicle |
| US8126612B2 (en) * | 2008-10-27 | 2012-02-28 | Concordia University | Steering system and method for independent steering of wheels |
| US8205892B2 (en) * | 2010-07-30 | 2012-06-26 | Deere & Company | Method of automatically changing wheel toe angle |
| US8480099B2 (en) * | 2011-06-13 | 2013-07-09 | Scott S. Porta | Apparatus and method for adjusting toe angle in the wheels of a solid axle |
| JP5738234B2 (en) * | 2012-05-30 | 2015-06-17 | 本田技研工業株式会社 | Rear wheel toe angle variable vehicle |
| CN106114614B (en) * | 2016-08-26 | 2018-05-18 | 吉林大学 | A kind of controlled hydraulic locking type left and right wheels independent steering gear |
| KR102104748B1 (en) * | 2019-05-14 | 2020-04-24 | 문윤경 | Apparatus for steering a vehicle |
| DE102022116729A1 (en) | 2022-07-05 | 2024-01-11 | Schaeffler Technologies AG & Co. KG | Actuator and chassis for vehicle |
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| JP2001097240A (en) | 1999-09-30 | 2001-04-10 | Toyota Autom Loom Works Ltd | Toe angle adjusting mechanism and steering device for wheel in vehicle |
| US6719311B2 (en) | 2001-03-01 | 2004-04-13 | Dana Corporation | Vehicle steering assembly |
| US6658334B2 (en) * | 2001-08-01 | 2003-12-02 | Delphi Technologies, Inc. | Static steering angle reducing algorithm for four wheel steering systems |
| JP2003087219A (en) * | 2001-09-07 | 2003-03-20 | Mitsubishi Cable Ind Ltd | Device and method for removing interference |
| JP2003087221A (en) * | 2001-09-13 | 2003-03-20 | Matsushita Electric Ind Co Ltd | Device and method for receiving and demodulating cdma |
| US6962356B2 (en) * | 2002-05-08 | 2005-11-08 | Mando Corporation | Active toe angle adjustment mechanism |
| EP1361087B1 (en) * | 2002-05-08 | 2014-08-06 | Mando Corporation | Active toe angle adjustment mechanism |
| JP2005297782A (en) * | 2004-04-12 | 2005-10-27 | Toyota Motor Corp | Toe angle adjustment mechanism |
-
2006
- 2006-09-12 KR KR1020060087860A patent/KR100748350B1/en active IP Right Grant
-
2007
- 2007-01-09 EP EP07000337A patent/EP1900603A1/en not_active Withdrawn
- 2007-01-30 JP JP2007018750A patent/JP2008068853A/en active Pending
- 2007-02-01 CN CNA2007100079916A patent/CN101143600A/en active Pending
- 2007-02-23 US US11/678,083 patent/US7325818B1/en not_active Expired - Fee Related
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101628528B (en) * | 2009-05-15 | 2011-03-23 | 邵延 | Wheel link structure |
| CN104512456A (en) * | 2013-09-27 | 2015-04-15 | 北汽福田汽车股份有限公司 | Automobile, power steering gear, and control method of power steering gear |
Also Published As
| Publication number | Publication date |
|---|---|
| KR100748350B1 (en) | 2007-08-09 |
| JP2008068853A (en) | 2008-03-27 |
| US7325818B1 (en) | 2008-02-05 |
| EP1900603A1 (en) | 2008-03-19 |
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